US5309944A - Electromagnetic proportional pressure reducing valve - Google Patents

Electromagnetic proportional pressure reducing valve Download PDF

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Publication number
US5309944A
US5309944A US08/064,198 US6419893A US5309944A US 5309944 A US5309944 A US 5309944A US 6419893 A US6419893 A US 6419893A US 5309944 A US5309944 A US 5309944A
Authority
US
United States
Prior art keywords
plunger
spool
pressure
solenoid
control port
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/064,198
Other languages
English (en)
Inventor
Satoshi Chikamatsu
Noboru Kurita
Koji Morita
Yoshiyuki Eto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
KYB Corp
Original Assignee
Kayaba Industry Co Ltd
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kayaba Industry Co Ltd, Nissan Motor Co Ltd filed Critical Kayaba Industry Co Ltd
Assigned to NISSAN MOTOR CO., LTD., KAYABA KOGYO KABUSHIKI KAISHA reassignment NISSAN MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ETO, YOSHIYUKI, MORITA, KOJI
Assigned to KAYABA KOGYO KABUSHIKI KAISHA, NISSAN MOTOR CO., LTD. reassignment KAYABA KOGYO KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHIKAMATSU, SATOSHI, KURITA, NOBORU
Application granted granted Critical
Publication of US5309944A publication Critical patent/US5309944A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding valves
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
    • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
    • G05D16/2024—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means the throttling means being a multiple-way valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated

Definitions

  • This invention relates to the fail-safe function of an electromagnetic proportional pressure reducing valve.
  • An electromagnetic pressure reducing valve as shown in FIG. 5 for example, comprises a solenoid 8 which causes a spool 1 to slide for connecting a control port 4 to either a supply port 5 or a tank port 6 depending on the slide position.
  • the spool 1 is inserted such that it is free to slide in a hole 2a in a valve housing 2.
  • the solenoid 8 is housed in a case 10 connected to the valve housing 2, and a plunger 9 is made to support the opposite end 1b of the spool 1 according to the magnetization state of the solenoid 1.
  • the solenoid 8 is magnetized, and the plunger 9 is thereby pulled toward a base 7 of the case 10 so as to push the spool 1 towards the left of the figure.
  • the pushing force in this case is proportional to the magnetizing current flowing through the solenoid 8.
  • the pressure Pc generated in the control port 4 varies according to the ratio of S 1 and S 2 . For example, when S 1 is small and S 2 is large, the pressure Pc increases.
  • a driving force F 1 acts on the spool 1 tending to push it toward the left of the figure. Further, as the pressure Pc acts on the left end of the spool 1 via the feedback oil passage 3, a pushing force F 2 based on this pressure Pc acts on the spool 1 in a right hand direction. If the pressure receiving surface area of the spool 1 is Aa, this pushing force is given by:
  • the spool 1 is thus held in a position at which the driving force F 1 due to the solenoid 8 and the pushing force F 2 acting in the reverse direction are balanced.
  • the driving force F 1 is proportional to the electric current i 1 flowing through the solenoid 8, while the pushing force F 2 is proportional to the pressure Pc generated by the control port 4.
  • the pressure Pc is therefore proportional to the current i 1 flowing through the solenoid 8.
  • the spool driving force F 1 of the plunger 9 varies, so the spool is displaced to a position at which the pushing force F 2 is in equilibrium with it, and the ratio of S 1 to S 2 varies.
  • the control port 4 is no longer to maintain the pressure, and the hydraulic actuator 20 shortens. If the actuator 20 is used in a hydraulic unit for distributing the driving force in a torque split type four-wheeled vehicle and power is no longer supplied to the solenoid 8 due to a fault in the electric circuit, therefore, four-wheeled drive becomes impossible.
  • the plunger 9 could be pulled toward the spool 1 by a spring so that even if the spool driving force F 1 dropped to zero when the solenoid magnetizing current i 1 was interrupted, the control port 4 maintained a certain minimum pressure, but in this case it would no longer be possible by ordinary means to set the pressure Pc of the control port 4 below this minimum level.
  • this invention provides a pressure reducing valve comprising a supply port connected to an oil source, a tank port connected to a tank, a control port connected to a hydraulic actuator, a spool connecting the control port to the tank port depending on its axial position, a first plunger in contact with one end of the spool, a first solenoid which drives the first plunger axially by means of a driving force according to an magnetizing current provided, and a feedback oil passage for applying the pressure of the control port to the opposite end of the spool, wherein the pressure generated by the control port is increased and decreased according to the magnetizing current of the first solenoid.
  • This valve further comprises a second plunger arranged in series with the first plunger, a spring which pushes the second plunger in the direction of the first plunger, and a second solenoid for pulling the second plunger in opposition to the restoring force of the spring such that it is not in contact with the first plunger when the second solenoid is magnetized.
  • the feedback passage is formed in the spool.
  • valve further comprises a pin having a pressure receiving surface area smaller than that of the spool which receives pressure from the feedback passage so as to support the opposite end of the spool.
  • FIG. 1 is a vertical sectional view of an electromagnetic proportional reducing valve according to a first embodiment of this invention.
  • FIG. 2 is a vertical sectional view of an electromagnetic proportional reducing valve according to a second embodiment of this invention.
  • FIG. 3 is a vertical sectional view of an electromagnetic proportional reducing valve according to a third embodiment of this invention.
  • FIG. 4 is a vertical sectional view of an electromagnetic proportional reducing valve according to a fourth embodiment of this invention.
  • FIG. 5 is a vertical sectional view of an electromagnetic proportional reducing valve according to the prior art.
  • a spool 1 is inserted in a hole 2a inside a valve housing 2 such that it can freely slide in the housing.
  • a control port 4 supply port 5 connected to an oil source P and tank port 6 connected to a tank T open into this hole 2a, and the pressure Pc generated by the control port 4 is controlled according to the position of the spool 1.
  • a throughhole 14 facing the rear of the plunger 9 is formed in the case 10, the tip of the second plunger 12 being inserted in this throughhole 14.
  • the second plunger 12 is held back against the force of a spring 13 such that it is not in contact with the first plunger 9.
  • a control current i 1 which varies according to a target pressure value of the control port 4 is supplied to the first solenoid 8, and a constant current i 2 , which is larger than the minimum current required to maintain the second plunger 12 held back against the force of the spring 13, is supplied to the second solenoid 11.
  • the control current i 1 which varies according to the target pressure is applied to the first solenoid 8, and the plunger 9 displaces the spool 1 due to the driving force produced. A pressure dependent on the position of the spool 1 is thereby generated by the control port 4, and normal pressure reduction control is performed.
  • control port 4 maintains a constant pressure, and a hydraulic actuator 20 can continue to support a load by means of this pressure.
  • the pressure Pc of the control port 4 can be reduced to the pressure of the tank port 6.
  • the pressure Pc of the control port 4 is then equivalent to the pressure of the tank port 6.
  • this hydraulic actuator 20 is used in a hydraulic unit which distributes the driving force in a torque split type vehicle having four wheel drive, and a fault occurs in the vehicle's electrical system, the minimum four wheel driving force can be maintained, and the driving force is distributed. This distribution would be in such a ratio that tight corner braking does not occur.
  • the plunger 12 withdraws to a position at which it no longer interferes with the first plunger 9, the position of the spool 1 is determined only by the first plunger 9 which is displaced according to the control current i 1 , and normal control is restored.
  • the pressure can be maintained simply by providing a second solenoid 11 as described hereintofore.
  • This arrangement therefore constitutes a simple fail-safe mechanism without any need to provide a special pressure maintaining valve in the hydraulic circuit.
  • basic pressure reduction characteristics are exactly the same as in a pressure reduction valve according to the prior art, there is no risk that reliability of valve operation will be impaired, and the pressure reducing valve can be manufactured at low cost.
  • the feedback oil passage 3 which applies the pressure Pc generated by the control port 4 to the end 1a of the spool 1, passes right through the spool 1. There is thus no need to provide the feedback oil passage 3 in the housing 2, and the structure of the pressure reducing valve can be made more compact.
  • FIG. 3 shows a third embodiment of this invention.
  • This valve has an "underlap" type of spool of which the sliding surface does not completely cover the supply port 5 and the tank port 6, and in this case also, the pressure Pc is controlled according to the position of the spool 1.
  • FIG. 4 shows a fourth embodiment of this invention wherein a reaction pin 15 having a pressure receiving surface area As less than the pressure receiving surface area Aa of the spool 1, is provided to apply the pushing force F 2 to the end 1a of the spool 1 according to the pressure Pc of the control port 4.
  • the pressure Pc of the feedback oil circuit 3 acts on the reaction pin 15, which then pushes the spool 1.
  • this pushing force F 2 is given by:

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Magnetically Actuated Valves (AREA)
  • Control Of Fluid Pressure (AREA)
US08/064,198 1992-05-19 1993-05-19 Electromagnetic proportional pressure reducing valve Expired - Fee Related US5309944A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP04126408A JP3110861B2 (ja) 1992-05-19 1992-05-19 電磁比例減圧弁
JP4-126408 1992-05-19

Publications (1)

Publication Number Publication Date
US5309944A true US5309944A (en) 1994-05-10

Family

ID=14934419

Family Applications (1)

Application Number Title Priority Date Filing Date
US08/064,198 Expired - Fee Related US5309944A (en) 1992-05-19 1993-05-19 Electromagnetic proportional pressure reducing valve

Country Status (3)

Country Link
US (1) US5309944A (de)
JP (1) JP3110861B2 (de)
DE (1) DE4316637C2 (de)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5878720A (en) * 1997-02-26 1999-03-09 Caterpillar Inc. Hydraulically actuated fuel injector with proportional control
US6198369B1 (en) 1998-12-04 2001-03-06 Tlx Technologies Proportional actuator for proportional control devices
US6392516B1 (en) 1998-12-04 2002-05-21 Tlx Technologies Latching solenoid with improved pull force
US6435213B2 (en) 1999-04-23 2002-08-20 Visteon Global Technologies, Inc. Solenoid operated hydraulic control valve
US20040079306A1 (en) * 2002-10-23 2004-04-29 Norton John D. Variable lift electromechanical valve actuator
WO2004102050A1 (de) * 2003-05-08 2004-11-25 Bosch Rexroth Ag Hubmagnetanordnung
US20050199295A1 (en) * 2004-03-10 2005-09-15 Martin Heusser Electrohydraulic control device
WO2006072377A1 (de) * 2005-01-07 2006-07-13 Voith Turbo Gmbh & Co. Kg Redundante elektrohydraulische ventilanordnung
US20070246111A1 (en) * 2006-04-19 2007-10-25 Santos Burrola Actuating valve with control port vent to ameliorate supply pressure fluctuation
US20080087345A1 (en) * 2006-10-16 2008-04-17 Caterpillar Inc. Direct operated cartridge valve assembly
US7513272B2 (en) * 2004-03-30 2009-04-07 Jtekt Corporation Solenoid valve
US20100154899A1 (en) * 2006-07-20 2010-06-24 Toyota Jidosha Kabushiki Kaisha Pressure control device
CN102213330A (zh) * 2010-04-01 2011-10-12 株式会社电装 螺线管滑阀
CN102235540A (zh) * 2010-04-01 2011-11-09 株式会社电装 螺线管滑阀
US8622048B2 (en) * 2010-04-05 2014-01-07 Stoneridge, Inc. Three-port valve
CN107461516A (zh) * 2017-08-02 2017-12-12 北京航空航天大学 一种差动式电液比例定差减压阀
CN107504213A (zh) * 2017-09-30 2017-12-22 中国第汽车股份有限公司 一种滑阀结构的比例溢流电磁阀及其工作方法
US9968033B2 (en) * 2016-06-21 2018-05-15 Macdon Industries Ltd. Crop machine with an electronically controlled hydraulic cylinder flotation system
GB2556379A (en) * 2016-09-06 2018-05-30 Camcon Auto Ltd Electromagnetic actuator
US20180334153A1 (en) * 2017-05-17 2018-11-22 Mando Corporation Valve assembly and anti-lock braking system including the same
CN111442007A (zh) * 2020-04-07 2020-07-24 上海诺玛液压系统有限公司 一种大流量直动式比例减压阀
US11358359B2 (en) 2015-07-03 2022-06-14 Sms Group Gmbh Hydraulic machine unit and method for operating such a machine unit
EP4592569A1 (de) * 2024-01-25 2025-07-30 Nabtesco Corporation Elektromagnetisches proportionalventil

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4402633A1 (de) * 1994-01-29 1995-08-03 Rexroth Mannesmann Gmbh Magnetbetätigtes Ventil, insbesondere magnetbetätigtes Vorsteuerventil
AUPM806794A0 (en) * 1994-09-12 1994-10-06 First Green Park Pty Ltd Improved lightweight load bearing base and packaging system for use therewith
US5579807A (en) * 1994-09-14 1996-12-03 Tec Tran Corporation Solenoid-operated pressure control valve
JP4025579B2 (ja) 2002-05-13 2007-12-19 株式会社ケーヒン 液圧制御装置

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807441A (en) * 1971-06-09 1974-04-30 Citroen Sa Electrically operated valves for delivering fluid under pressure
US4250922A (en) * 1978-05-24 1981-02-17 Robert Bosch Gmbh Electromagnetically operated control valve

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3345561A1 (de) * 1983-12-16 1985-07-11 Gräber, Peter, 7541 Straubenhardt Gasdruckregler-sicherheitsmagnetventil-kombination

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807441A (en) * 1971-06-09 1974-04-30 Citroen Sa Electrically operated valves for delivering fluid under pressure
US4250922A (en) * 1978-05-24 1981-02-17 Robert Bosch Gmbh Electromagnetically operated control valve

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5878720A (en) * 1997-02-26 1999-03-09 Caterpillar Inc. Hydraulically actuated fuel injector with proportional control
US6198369B1 (en) 1998-12-04 2001-03-06 Tlx Technologies Proportional actuator for proportional control devices
US6392516B1 (en) 1998-12-04 2002-05-21 Tlx Technologies Latching solenoid with improved pull force
US6435213B2 (en) 1999-04-23 2002-08-20 Visteon Global Technologies, Inc. Solenoid operated hydraulic control valve
US20040079306A1 (en) * 2002-10-23 2004-04-29 Norton John D. Variable lift electromechanical valve actuator
WO2004102050A1 (de) * 2003-05-08 2004-11-25 Bosch Rexroth Ag Hubmagnetanordnung
US20060114089A1 (en) * 2003-05-08 2006-06-01 Bosch Rexroth Ag Solenoid assembly
US7145424B2 (en) 2003-05-08 2006-12-05 Bosch Rexroth Ag Solenoid assembly
US7320335B2 (en) * 2004-03-10 2008-01-22 Hawe Hydraulik Gmbh & Co. Kg Electrohydraulic control device
US20050199295A1 (en) * 2004-03-10 2005-09-15 Martin Heusser Electrohydraulic control device
US7513272B2 (en) * 2004-03-30 2009-04-07 Jtekt Corporation Solenoid valve
WO2006072377A1 (de) * 2005-01-07 2006-07-13 Voith Turbo Gmbh & Co. Kg Redundante elektrohydraulische ventilanordnung
US8096321B2 (en) 2005-01-07 2012-01-17 Voith Turbo Gmbh & Co. Kg Redundant electrohydraulic valve system
US20090000672A1 (en) * 2005-01-07 2009-01-01 Voith Turbo Gmbh & Co. Kg Redundant Electrohydraulic Valve System
US20070246111A1 (en) * 2006-04-19 2007-10-25 Santos Burrola Actuating valve with control port vent to ameliorate supply pressure fluctuation
US20100154899A1 (en) * 2006-07-20 2010-06-24 Toyota Jidosha Kabushiki Kaisha Pressure control device
US8061384B2 (en) 2006-07-20 2011-11-22 Toyota Jidosha Kabushiki Kaisha Pressure control device
EP2045495A4 (de) * 2006-07-20 2010-12-22 Toyota Motor Co Ltd Drucksteuerungsvorrichtung
US7766042B2 (en) * 2006-10-16 2010-08-03 Caterpillar Inc Direct operated cartridge valve assembly
US20080087345A1 (en) * 2006-10-16 2008-04-17 Caterpillar Inc. Direct operated cartridge valve assembly
CN102235540A (zh) * 2010-04-01 2011-11-09 株式会社电装 螺线管滑阀
CN102213330A (zh) * 2010-04-01 2011-10-12 株式会社电装 螺线管滑阀
US8622048B2 (en) * 2010-04-05 2014-01-07 Stoneridge, Inc. Three-port valve
US11358359B2 (en) 2015-07-03 2022-06-14 Sms Group Gmbh Hydraulic machine unit and method for operating such a machine unit
US9968033B2 (en) * 2016-06-21 2018-05-15 Macdon Industries Ltd. Crop machine with an electronically controlled hydraulic cylinder flotation system
GB2556379A (en) * 2016-09-06 2018-05-30 Camcon Auto Ltd Electromagnetic actuator
US20180334153A1 (en) * 2017-05-17 2018-11-22 Mando Corporation Valve assembly and anti-lock braking system including the same
US11066054B2 (en) * 2017-05-17 2021-07-20 Mando Corporation Valve assembly and anti-lock braking system including the same
CN107461516A (zh) * 2017-08-02 2017-12-12 北京航空航天大学 一种差动式电液比例定差减压阀
CN107504213A (zh) * 2017-09-30 2017-12-22 中国第汽车股份有限公司 一种滑阀结构的比例溢流电磁阀及其工作方法
CN107504213B (zh) * 2017-09-30 2019-05-31 中国第一汽车股份有限公司 一种滑阀结构的比例溢流电磁阀及其工作方法
CN111442007A (zh) * 2020-04-07 2020-07-24 上海诺玛液压系统有限公司 一种大流量直动式比例减压阀
EP4592569A1 (de) * 2024-01-25 2025-07-30 Nabtesco Corporation Elektromagnetisches proportionalventil

Also Published As

Publication number Publication date
JPH05324092A (ja) 1993-12-07
DE4316637C2 (de) 1996-09-05
JP3110861B2 (ja) 2000-11-20
DE4316637A1 (de) 1993-11-25

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